Reheat turbine control



3 Slieets-Sheet 1 Filed June 1949 w fi m mvm N HNDI N ew QQQQ Oz HOO w sHH \..no\ QHH S k a Nbfix W I IILI E WWPHN UQKKO m 5 um f \N 04 m m 0 Y m R m @m o m m M 5 Q July 11, 1950 o. N. BRYANT 2,514,931

REHEAT TURBINE CONTROL Filed June 25, 1.948 3 Sheets-Sheet 2 rlL INVENTOR OZRO N .BRYHNT ATTORNEY Patented July 11 1950 anger 3 Claims.

' This a-pplication is a. continuation-in-part of m application SerialfNo; 36,837, ,filed July 3,

1948, Patent No; 2,504,640, granted April 18, 1950.

' The invention relates to'a, turbine installation ini'wliichsuperheated steam issupplied to a first or high-pressure turbine section and steam discharging from the latter is reheated and then supplied to a second or intermediate-pressure turbinerzisectiomand it has for an object to provide' for operation of the throttle and the admission: or governor valves in the supply connection of 'the first turbine section andof the interceptor valve in thesupply connection of the second turbine section'in response to turbine speed.

Prifurther object of the invention is to provide, for an installation of the above character, a

governing system consisting, in effect, of two governors', a normal or main one set to govern the turbine installation for normal speed and an auxiliary one set to supersede the first governor at a speed slightly higher than normal to take control ofthe" admission valve to closethe latter upon a further. small percentage of, increase in speed followedpin theevent of slight additional increase in speed,.by rapid closing of the interceptor valve.

Another object oi the invention is to provide "for operation of the interceptor valve of a reheat turbine installation both in response to a governor set for a speed higher than normal and to an emergency or autostop governor, the governor having the setting fora speed above norrnal bei'ngs' capable of opening, and closing the interceptorvalve, and the emergency or autostop governormoperating, in theevent of a predetermined overspeed, to close the-interceptor valve aswell a's the' throttle valve, 1 I

Another object of the invention is to provide areheat turbine installation with an interceptor valve between thereheater and the section of the turbine supplied thereby together with a governorset for a speed above normal and effective to close the interceptor valve in the event of sudden" drop in load to avoid increase in speed 's'ufiicientto operate the: emergency or autostop go ernor.

. The foregoing and other objects are efiected by the invention'as will be apparent from the following description and claims taken in connection. with. the accompanying drawings, forming a part of this application, in which: n

Fig. 1 is a diagrammatic view of (a boiler and reheat turbine installation; I I

Fig. 2 is a sectional view of the turbine control necha-nism, including the main and auxiliary 7'VUNIT'EVISTATES PATENT 2 governors and the throttle, cepting valves;

Fig. 3 is a sectional detailview showing a throtadmission and intertlevalve operating mechanism;

Fig. 4' is a diagram showing governor relations with respect to speed and load;

Fig. 5 is a sectional view showing main and auxiliary governors similar to Fig. 2 except for the modified an'dpreferred interceptor connection; and v Fig. 6 is a sectional view showing main and auxiliary governors of the inverse type.

In the drawings there are shown a boiler installation, at H], and a turbine installation, at H.

The boiler installationincludes a superheater I 2 and a reheater I l.

The turbine installation comprises a first or high-pressure unit or section 15 and a second or intermediate-pressure section or unit I6.

A passage I 1 delivers steam from the superheater to the high-pressure turbine section l5 and it includes a throttle valve l8 and a governor valve 19. A passage 2| conducts steam, exhausting from the high-pressure turbine section l5, through the reheater M to the intermediate-pressure turbine section I6, and an interand the intermediate turbine section.

v The governing or admission valve [9 and the interceptor va1ve 22 are operated in response to speed of the turbine installation. To this end, there are provided main and auxiliary governors, at 24, and, at 25, having force impressed thereon and varying. substantially as the square of the speed and an autostop emergency governor, at 26, which is tripped upon attainment of a predetermined overspeed. I

The main governor, at 24, is set for anormal speedand it operates to control the governing or admission valve I9. The auxiliary governor, at 25, isset for aslightly higher speed than the governor, at 24; and, because, as indicated in Fig. 4, the droop in speed for the auxiliary governor is less than that for the main governor, upon increase in speed of the installation to a predetermined small extent and within the governing range of, the main governor, at 24, the latter is superseded bythe auxiliary governor, at 25, not only to control the governing or admission valve but also, for slight increase in speed above that required to close the governor valve, to trip the intercepting valve 22 for closing.

, Tripping of the autostop governor, at 26, brings about closing of the interceptor valve 22 and of the throttle valve l8.

higher than that of the main governor, then, up-- on the turbine speed reaching 101 the auxil iary governor supersedes the main governor and closes the governor valve at 103% speed;'and,'

upon slight additional increase in speed, rapid closure of the intercepting valve 22 is initiated.

Just as soon as the speed drops belowfl03%,"

opening of the intercepting valve begins. Therefore, the auxiliary governor, at 25, takes care of transient or sudden load drops which might otherwise result in increase in speed, particularly on account of trapped steam, to an extent sufiicient for tripping by the autostop governor, in which event, time is required for resetting of the latter and for restoration of the installation to the line. Hence, the auxiliary governor, at 25, guards against operation of the autostop or emergency governor and inconvenience caused thereby except when required by emergency speed conditions.

As shown, the primary governing force or pressure is developed by the impeller 28 carried by the turbine shaft and developing pressure of oil varying substantially as the square of the speed. The impeller delivers oil under pressure to the chambers 23 and 33 of the main and auxiliary transformer governs, at 24, and, at 25, for action on the pressure areas 3| and 32 of the heads 33 and 34 of the bellows elements 35 and 3B. The bellows heads have thrust engagement with the stems 31 and 38 of the cup valves 39 and 40 covering escape ports 41 and 42 of spaces or passages 13 and E4 supplied by orifices 45 and 56 from a suitable oil pressure source. Springs 41 and 48 exert forces on the heads 33 and 34 so that each of the transformer governors has an equilibrium position with the primary or impeller fluid pressure 'force exerted on the bellows head balanced by the forces of the spring and of the secondary or transformed oil pressure acting on the cup valve and tending to open it.

The transformer governors, at 23, and, at 25, are provided with speed changers 53 and 5l so that the main governor, at 24, may be set for a normal operating speed and the auxiliary governor, at 25, may be set for a slightly higher speed. Also, the auxiliary governor, at 25, has a speed compensator to narrow its regulation so that the overnor valve may be fully closed at a speed which is only a small percentage above normal and so that, with only a slight further increase in speed, the intercepting valve may be closed.

The speed corrector or compensator is preferably of the type illustrated and described in my Patent No. 2,323,115 of June 29, 1943. It comprises a piston 53 connecting the cup valve and the stem 38, the piston providing a pressure area 54 opposing that of the cup valve 40 and exposed to pressure of liquid supplied by the passage 55 from the viscous orifice device, at 56, whose inlet is in communication with the space or passage, at 4'4. The orifice device provides for a pressure at 55 which is always proportional to the pressure at 44 dependent on the length of the helical viscous flow passage between the passage, at 44, and the passage, at 55. In operation, the governor, at 25, responds instantly to change in load with change in speed and the application of a proportional change of pressure to area 54 is effective to reduce the speed change due to load change. Therefore, the auxiliary governor, at 25, has, because of the compensating feature, a narrow percentage of regulation, and it is for this reason that it is capable, after superseding the main governor, at 24, of closing the governor valve upon a small percentage of increase in speed above normal and then, upon a slight additional increase in speed, to trip theinterceptor valve for closing, whereby the governor and interceptor valves are 1 controlled to prevent, pursuant to drop in load,

over-speeding of the turbine installation suflicient to operate the autostop governor.

Superseding of the main transformer governor, at 24, bythe auxiliary transformer governor, at 2 5, is effected by means of check valves 58 and 59 through which communication takes place with the control pressure passage or space 60 in which change in pressure is effective to operate the governor or admission valve l9 and to trip the interceptor valve 22 for closing movement. It will be apparentv that the check valves provide for the maintenance of pressure in the space Ell which is the higher of the transformed pressures developed by the main and auxiliary governors, at 2 4, and, at 25. Therefore, when the turbine speed increases slightly above normal, for example, to 101%, the auxiliary governor, at 25, takes over control of the admission valve. As the regulation of the latter governor is small, further small increase in speed, for example, to

103%, suffices to close the governor valve l9 and a slight additional increase in speed trips the interceptor valve 22 for closing.

The governor valve I9 is of a conventional type and it is operated by the hereinafter-described servo-motor, at 52, having a relay B3 operative in response to pressure in the control passage or space 60. i a

shown, it may comprise the servo-motor, at 64,

including a cylinder 65, a piston 66 inthe cylinder connected by means including its rod 61 to the valve, and a spring 68 exerting force on the piston 66 to close the valve. The intercepting valve 22 is opened by fluid under pressure supplied to the cylinder 55 and acting on the piston 66 against the spring 68. Fluid pressure for this purpose is provided in the space or passage 59 supplied. through an orifice H from any suitable pressure source.

The space or passage 69 communicates with the cylinder 12 unitary and coaxial with the cylinder and having a piston. 13 therein. A hollow stem 14 depends from the piston 13, encompasses the rod 61, and is provided with a cup valve 15 at its lower end, the cup valve being in covering relation with respect to the ports 6 formed in the piston 56.

Increase in pressure in the cylinder 12 'isefiective to restrict the escape of liquid through the ports 15 from below the piston 56, in consequence of which the fluid pressure builds up below such piston and opens the intercepting valve Preferably, the piston 13 and the cup valve 15 defiri annular orificesfl qif and '18 with" respectto I the-rodtoassure, with new, of higher pressure tendingto restrict the escape of iiquidfrom below the piston than" that tending to openthe cup {valve to? provide forsuchescape. Oh the other "the piston downwardly, the pressure of liquid belowthe piston actingag'ainstthe cup Valve to o ehthe latter, wherehyliduid is-permitted to escape-tothe spaceabovethepiston= for" discharge through th'e'dr'ain connect-1011 95 4 From the structure'described', it will be apparent that drop in pressure in the space 69 renders the spring fit 'e'ffective to close the intercepting valve 22' wholly or partially. Therefore, when the p'ressurereaches' a' value corresponding to slightly more than-103 speed; the trip relay, at QUE-is operatedth release the pressure inthe interceptor va-lve Operating devicepressure" space. Also, the autostop governor operatesto release such pressure. The trip relay, at =st-is-preferably comprised by a cylinder- 8-1; a piston S Z'in-the cylinder connected to*the-valve-83i and aspring 84 exerting force onthe-patents close the valve. As the passageel suppliesliquid under control pressure tot-he cylinder for action on-the piston- 8! against the spring '84; it-willbe"apparent-that the latter may be set-,- for example, by the screw 85, for openingof the valve 83 when the control pressure reachesa-value'slightly in-exce'ss of that requiredfor closing the governor or admission valve;- whereupon thepressure in the space 69 c ist'rippe'd or released and the spring 63' rapidly closes theinterceptor'valve"2-23 In-theevent or overspeeding Of the installation acts on the piston 99 carriedthe r'od- 100 455? tendihg from-opposite sides tn'ereor.- The upper end of th'erod is connected, through a tension springJ-Bl"; to t-he follow-up" lever I02 pivotally connected to the operating piston and governor valve linkage. T-li'elowe'r end of the rod 100 carries a cup valve 104- covering the bore l 65 formed in the pilotvalve and in open communication with the-drain passage I06. I

"rile-upper end of thepilotvalve has a piston area- PM exposed to pressure in th chamber lllt suppliedfrom a suitable pressure source through the erifice l fl'g. Therefore, pressure in the chamberroe-exerts force on the 'pilot valve in the tothe' extent of about 10%,theaut'ostop governor,

at 2631's tripped to relieve suddenly' the pressure in the space or passage" 69 whereupon the interceptor valve rapidlycloses. Also; operation'of the-ahtostop' governc-ris effective to'relieve the pressure in space 88-, supplied by the orifice 89; for=rapid-closing of the-throttlevalve 1'3 so that, in theevent of' an emergency condition, both the throttle and-interceptorvalves are'closed;

Po-provide for closing'only of theinterceptor val'v'efirr response to' governor pressure and for closing of boththethrottle and interceptor valves in response to-autostop governor operation; the autostopline QUF'is connected; through checkvalves- 9+ and 9-2; to the spaces- 69' and 88 and which -checlevalvesare arranged-to open to drop the'pre'ssure-inboth spaces when-the pressure in line 90- is dumped by opening of the autostop valve: w

Therelative' operations-willbe-clearer from a considerationof Fig. 4, relating-speedor cycles to load. In-- this view, lines a and 12- represent speed droop *from no load to"full load for the main and auxiliary governors; line 0 represents speed-for operation oftrip relaytfl; and line 12 indicates-speed for throttle valve tripping in response toemergency or autostop governor operation-.=- The servo-motor at-tz for perating the governorvalve l9 is more particularly disclosed and claimed in- Schwendner Patent No.- 2,224,321, granted December 10,1940. It includesthe operating piston 95 in the cylinder 96 connected by the link-age 91- to 'the valve l9; The pressureresponsive relay, at- 63, includes a pilot valve 98 for controlling the admission and exhaust of mo tivefiuid to" opposite sides of the operating piston 95'; Governor pressure'supplied tothe space 65 directionto move'it away from the cup valve, 'While'thespring llll exertsfor'ce thereon irl'the direction-to mov the pilot valve toward the'cup' valve. It will be'obvious, therefore, that the'pilot valve seeks aposition with the fluid pressure and springforces balanced.

' As the governing pressure force appliedto the piston 99- is opposedby the force of th spring Ifll acting: thereon, upon a change-in governing pressure supplied to the space 60, the piston 99 moves, in co-ns'equenceof which the cup valve I64 is moved to change the pressure in the chamber H13 and thereby cause movement of the pilot valve, motion of the pilot Valve following that of the cup'valve; Thus, it will beseen that the pressure-responsive piston and cup valve, instead of being subjected to the load required to move the pilot valve, serve only to control the application ofpower for that purpose, whereby the pressureresponsive piston is relieved entirely of any resist-ancetto movement of the-p'ilotvalve.

While ordinarily the apparatus so far specifically; shown and described would restrict operationof the interceptor valve to the auxiliary governor, nevertheless, as the passage 6| communicates with the space 60, the main governor 24 may, .under certain conditions,.such as a lower load setting or system frequency variation, develop suihcient pressure to release the interceptor valve. To avoid this undesired possibility, in Figs. 15 and6, the triprelay pressure supply pas sages Gla and 6|b, instead of communicating withthe. pressure space 60 supplied by either governor, are respectively connected to the auxiliary means, the trip relay, at 8B- or atllila, is removed entirel from the possibility of any influence by the main governor- Fig. 6 shows a form of the invention wherein the governor pressures change inversely in relation tospeed. In Figs. 2 and 5, increase in speed is accompanied by increase in impeller or primary pressure and increase in secondary or governor pressure, the change in secondary or governor pressure being maintained in proportional relation to primary pressure change. tionality. of pressure changes also exists where the changes are in inverse relation, that is, if the primary pressure increases incident to an increase in speed, the secondary pressure decreases and vice versa.

An inverse arrangement is shown in Fig. 6. As compared to the direct arrangement, the inverse one involves certain mechanical changes to establish the inverse relation and modification of the interceptor valve trip relay.

Referring more particularly to Fig. 6, the main and auxiliary governors 24a and 25a, include levers] I2 and H3 fulcrumed at lie and H5; The outer ends of the levers engage cup valves 39 Proporand 40a." The pressure abutments' 3la-and 32a, subject to primary or impeller pressure, exert forces, through the thrust rods H6 and H1, on the levers H2 and H3 in opposition to forces of the springs 41d and 48a exerted thereon, the spring forces being subject to adjustment by the speed changes at 50a and 5la.

Since the main and auxiliary governors are similar, except fOr the compensating or speed adjusting feature of the auxiliary governor, the description of the operation of one will suifice for both. Assuming an increase in impeller pressure due to an increase in turbine speed, the increase in such pressure acting on the area 3la exerts force on the lever H2 in the direction to movethe latter upwardly against the force of the spring 41a thereby reducing the force or pressure of the spring tending to move the cup valve 390, in the direction to increase the secondary pressure in the space or passage 43a in consequence of which the secondary pressure in such space will be decreased. Thus, a change in primar 0r impeller pressure is accompanied by a proportional or inverse change in secondary pressure, the relationship of the changes being fixed by the pressure areas of the abutment 3la and of the cup valve 39a.

In the inverse arrangement shown, governor pressure is applied below-the relay pressure-responsive piston 99a and the rod [00a abuts a compression spring lfila. engaging the follow-up lever 1211.

Instead of the speed-correcting pressure in the passage 55 supplied from the viscous orifice 56 being applied directly to the cup valve to move the latter in the direction to efiect a further change in secondary pressure, as in Fig. 2, in Fig. 6, the passage 55a, supplied from the secondary pressure space 44a through the viscous orifice device 56a, applies pressure to a piston 120 engaging one end of the spring l2! whose other end engages the lever H3 to exert closing force on the cup valve 40a.

The modified form of speed-correotor or compensator in Fig. 6 operates as follows: Assuming a reduction in load and an increase in impeller pressure incident to increase in speed, the secondary pressure decreases proportionally; however, the speed change required for the load change is reduced by applying a proportional part of the pressure change to the piston I20, in consequence of which the force exerted by the sprin [2! on the cup valve in the closing direction of the latter will be reduced, thus eflecting further decrease in secondary pressure, so that, for a given change in secondary pressure, a smaller change in impeller or primary pressure is required, that is, the speed change for the load change is reduced.

Since, with the inverse arrangement shown in Fig. 6, a drop in load is accompanied by a decrease in secondary or governing pressure, the trip valve 83a is arranged, upon sufficient drop in pressure, to release the pressure holding the interceptor valve open. To this end, the trip valve 830. of Fig. 6 is reverse of the trip valve 83 shown in Figs. 2 and 5, that is, instead of drop in pressure resulting in closing of the valve 83, as in Figs. 2 and 5, in Fig. 6, drop in pressure results in opening of the valve 83a.

From the foregoing, it will be apparent that I have provided admission and interceptor valves for a reheat turbine installation with the admission valve controlled by a main governor for norincl Sp d operat on to ether with an auxiliary governor having a slightly higher speed setting than the main governor and arranged, upon slight increase in speed above normal, to supersede the latter so that, with a small further increase in speed, the governor valve may be closed; and, with a slight additional increase in speed, the relay, at or 80a, may be tripped to brin about rapid closing of the interceptor valve. The autostop governor not only closes the throttle valve but also the interceptor valve. The auxiliary governor, therefore, operates to keep the reheat turbine installation under control with load drops which might otherwise result in operation of the autostop governor with the inherent inconvenience of the latter so far as restoring the installation to the line is concerned.

While the invention has been shown in a plurality of forms, it will'be obvious to those skilled in the art that it is not so limited, but is susceptible of various changes and modifications without departing from the spirit thereof.

What is claimed is:

1 In a turbine installation wherein superheated steam is supplied to a first turbine section and the steam discharging from the latter is reheated and then supplied to a second turbine section, the combination of, main and auxiliary governors driven by the turbine; means including an emergency governor for shutting ofi the supply of steam to the turbine upon the attainment of a predetermined overspeed; a governor valve in the supply connection or the first turbine section and controlled in response to said main and auxiliary governors; an interceptor valve in the reneated steam supply connection of the second turbine section; means for biasing the interceptor valve to closed position; means Ior holding the interceptor valve open against the biasing means; speed changers for the main and auxiliary governors; means providing i'or small speed droop of the auxiliary governor relative to the main governor so that, with the auxiliary governor speed changer set Ior a slightly higher speed than the main governor speed changer and the attainment of Sufncient turbine speed, the auxihary governor takes control of the turbine; and means responsive solely to the auxiliary governor at a turbine speed in excess or that required for it to close the governor valve, but below that required Ior emergency governor operation, to release said means for holding the interceptor valve open.

2. In a turbine installation wherein superheated steam is supplied to a n'rst turbine section and the steam discharging .lrom the latter is reneated and then summed. to a second turbine section, the combination of, main and auxiliary governors driven by the turbine and each operative to provlde a control pressure which varies directly as a function OI turbine speed; means including an emergency governor for shutting on the supply or steam to the turbine upon the attainment of a predetermined overspeed; a governor valve in the supply connection or" the first turbine section; an interceptor valve in the reheated steam supply connection tor the second turbine section; means for biasing the interceptor valve to closed position; means for holding the interceptor valve open against the biasing means; a servo-motor responsive to the higher of said control pressures to control the governor valve; pressure-responsive means for releasing said means Ior holding the interceptor valve open; means including a check valve for restricting response or said pressureresponsive means to the auxiliary governor control pressure; speed changers for the main and auxiliary governors; and means providing for small speed droop of the auxiliary governor relative to the main governor so that, with the auxiliary governor speed changer set for a slightly higher speed than the main governor speed changer and the attainment of sufiicient turbine speed, the auxiliary governor control pressure takes control of the turbine and, at a turbine I speed in excess of that required to close thegovernor valve, but below that required for emergency governor operation, renders the pressureresponsive means effective to release said means for holding the interceptor valve open.

3. In a turbine installation wherein superheated steam is supplied to a first turbine section and the steam discharging from the latter is reheated and then supplied to a second turbine section, the

combination of, main and auxiliary governors I driven by the turbine and each operative to provide a control pressure which varies inversely as a function of turbine speed; means including an emergency governor for shutting off the supply of steam to the turbine upon the attainment of a predetermined overspeed; a governor valve in the supply connection of the first turbine section; an interceptor valve in the reheated steam supply connection of the second turbine section; means for biasing the interceptor valve to closed position; means for holding the interceptor valve open 10 against the biasing means; a servo-motor responsiVe to the lower one of said governor control pressures to control the governor valve; pressureresponsive means for releasing the holding means; means including a check valve for restricting response of said pressure-responsive means to auxiliary governor control pressure; speed changers for the main and auxiliary governors; and means a providing for small speed droop 0f the auxiliary REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Name Date Bryant Apr. 18, 1950 Numb er 2,504,640 

